EP2513489B1 - Mid-span gas bearing - Google Patents
Mid-span gas bearing Download PDFInfo
- Publication number
- EP2513489B1 EP2513489B1 EP10787786.2A EP10787786A EP2513489B1 EP 2513489 B1 EP2513489 B1 EP 2513489B1 EP 10787786 A EP10787786 A EP 10787786A EP 2513489 B1 EP2513489 B1 EP 2513489B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gas
- bearing
- compressor
- bearings
- centrifugal compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000007789 gas Substances 0.000 claims description 147
- 238000000034 method Methods 0.000 claims description 20
- 230000006835 compression Effects 0.000 claims description 15
- 238000007906 compression Methods 0.000 claims description 15
- 238000007789 sealing Methods 0.000 claims description 7
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 6
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 4
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 claims description 4
- 230000007246 mechanism Effects 0.000 claims description 4
- 239000012535 impurity Substances 0.000 claims description 3
- RWSOTUBLDIXVET-UHFFFAOYSA-N Dihydrogen sulfide Chemical compound S RWSOTUBLDIXVET-UHFFFAOYSA-N 0.000 claims description 2
- OTMSDBZUPAUEDD-UHFFFAOYSA-N Ethane Chemical compound CC OTMSDBZUPAUEDD-UHFFFAOYSA-N 0.000 claims description 2
- 230000000740 bleeding effect Effects 0.000 claims description 2
- 239000001273 butane Substances 0.000 claims description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 2
- 239000001569 carbon dioxide Substances 0.000 claims description 2
- 229910000037 hydrogen sulfide Inorganic materials 0.000 claims description 2
- 239000003949 liquefied natural gas Substances 0.000 claims description 2
- IJDNQMDRQITEOD-UHFFFAOYSA-N n-butane Chemical compound CCCC IJDNQMDRQITEOD-UHFFFAOYSA-N 0.000 claims description 2
- OFBQJSOFQDEBGM-UHFFFAOYSA-N n-pentane Natural products CCCCC OFBQJSOFQDEBGM-UHFFFAOYSA-N 0.000 claims description 2
- 239000001294 propane Substances 0.000 claims description 2
- 238000001914 filtration Methods 0.000 claims 1
- 230000008569 process Effects 0.000 description 12
- 239000012530 fluid Substances 0.000 description 8
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 230000003321 amplification Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- BWGNESOTFCXPMA-UHFFFAOYSA-N Dihydrogen disulfide Chemical compound SS BWGNESOTFCXPMA-UHFFFAOYSA-N 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001066 destructive effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/057—Bearings hydrostatic; hydrodynamic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
- F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/059—Roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2210/00—Working fluids
- F05D2210/10—Kind or type
- F05D2210/12—Kind or type gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/50—Bearings
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Definitions
- Exemplary embodiments relate generally to compressors and, more specifically, to a mid-span gas bearing in a multistage compressor.
- JP 2003 293987 A discloses fluid machinery having a rotor for feeding gas in a generally radial direction. Bearings are disposed on the rotor at both ends and a second bearing is disposed between the bearings.
- a compressor is a machine which increases the pressure of a compressible fluid, e.g., a gas, through the use of mechanical energy.
- Compressors are used in a number of different applications and in a large number of industrial processes, including power generation, natural gas liquification and other processes.
- compressors used in such processes and process plants are the so-called centrifugal compressors, in which the mechanical energy operates on gas input to the compressor by way of centrifugal acceleration, for example, by rotating a centrifugal impeller.
- Centrifugal compressors can be fitted with a single impeller, i.e., a single stage configuration, or with a plurality of centrifugal stages in series, in which case they are frequently referred to as multistage compressors.
- Each of the stages of a centrifugal compressor typically includes an inlet volute for gas to be compressed, a rotor which is capable of providing kinetic energy to the input gas and a diffuser which converts the kinetic energy of the gas leaving the impeller into pressure energy.
- Compressor 100 includes a shaft 120 and a plurality of impellers 130 - 136 (only three of the seven impellers are labeled).
- the shaft 120 and impellers 130 - 136 are included in a rotor assembly that is supported through bearings 150 and 155.
- Each of the impellers 130 - 136 which are arranged in sequence, increase the pressure of the process gas. That is, impeller 130 may increase the pressure from that of gas in inlet duct 160, impeller 131 may increase the pressure of the gas from impeller 130, impeller 132 may increase the pressure of the gas from impeller 131, etc.
- Each of these impellers 130 - 136 may be considered to be one stage of the multistage compressor 100.
- the multistage centrifugal compressor 100 operates to take an input process gas from inlet duct 160 at an input pressure (P in ), to increase the process gas pressure through operation of the rotor assembly, and to subsequently expel the process gas through outlet duct 170 at an output pressure (P out1 ) which is higher than its input pressure.
- the process gas may, for example, be any one of carbon dioxide, hydrogen sulfide, butane, methane, ethane, propane, liquefied natural gas, or a combination thereof.
- the pressurized working fluid within the machine (between impellers 130 and 136) is sealed from the bearings 150 and 155 using seals 180 and 185.
- a dry gas seal may be one example of a seal that can be used. Seals 180 and 185 prevent the process gas from flowing through the assembly to bearings 150 and 155 and leaking out into the atmosphere.
- a casing 110 of the compressor is configured so as to cover both the bearings and the seals, and to prevent the escape of gas from the compressor 100.
- the shaft becomes flexible therefore decreasing the rotor natural frequencies.
- the decrease in the fundamental natural frequencies of the rotor assembly tends to make the system more susceptible to rotor-dynamic instability, which can limit the operating speed and output of the machine.
- the other issue is the forced response due to synchronous rotor imbalance.
- the machine When the operating speed coincides with a rotor natural frequency, the machine is defined to be operating at a critical speed, which is a result of rotor imbalance.
- the compressor must pass through several of these natural frequencies or critical speeds before reaching the design operating speed.
- Systems and methods according to these exemplary embodiments provide for an increase in the number of stages in a centrifugal compressor while overcoming problems typically associated with such an increase.
- a centrifugal compressor includes a rotor assembly having a shaft and a plurality of impellers, a pair of bearings located at ends of the shaft and configured to support the rotor assembly, a sealing mechanism disposed between the rotor assembly and the bearings, and a first gas bearing disposed between the plurality of impellers and configured to support the shaft.
- the first gas bearing receives a working gas from an impeller located downstream from the location of the first gas bearing.
- a method of processing a working gas in a centrifugal compressor includes providing the working gas to an inlet duct of the compressor, processing the gas through a plurality of compression stages with each stage increasing the speed of the gas, bleeding a portion of the accelerated gas after a stage that is downstream from a midway point of the compression stages, providing the bled gas to a bearing, reintroducing the gas from the bearing to the working gas flowing in the compressor, and expelling the working gas from an outlet duct of the compressor.
- a centrifugal compressor includes a rotor assembly having a shaft and a plurality of impellers, a pair of bearings located at ends of the shaft and configured to support the rotor assembly, a sealing mechanism disposed between the rotor assembly and the bearings, and a plurality of gas bearings disposed between the plurality of impellers and configured to support the shaft.
- the gas bearings receive a working gas from respective impellers located downstream from a location of the gas bearings.
- a mid-span bearing may be utilized to provide additional stiffness to the rotor assembly with a longer shaft to overcome the critical speed issue highlighted above.
- Such a bearing makes the rotor assembly less flexible and therefore allows the rotor-dynamic energy (due to synchronous rotor imbalance forces) to be transmitted to the bearings.
- This "three-bearing" configuration increases the damping in the rotor modes and lowers amplification factors as the rotor traverses through the critical speed allowing for safe operation of the rotor assembly.
- a mid-span bearing may, therefore, be provided within the casing for facilitating an increased number of stages (i.e. longer shaft) and overcoming the rotor dynamic instability.
- Surface speed of a shaft is a function of its diameter.
- the diameter in the middle portion of the shaft is greater than the diameter at the end portions.
- the difference in speeds between these portions may be in the order of 2 to 3 times. Therefore, the surface speed of a shaft is greater (by a factor of 2 to 3) at the center portion of the shaft than it is at the end portions.
- Bearings such as bearing 150 and 155 of FIG. 1 may typically be oil bearings. Oil bearings, however, are limited to usage where surface speed is typically closer to the surface speed at end portions of the shaft.
- a mid-span bearing according to exemplary embodiments may be a gas bearing. Gas bearings can be used where surface speed is closer to the surface speeds at middle portions of a shaft.
- Oil bearings also require sealing systems for preventing leakage of oil into the gas being processed by the compressor. Gas bearings obviate this need for sealing systems.
- FIG. 2 illustrates a compressor according to exemplary embodiments.
- Compressor 200 includes a shaft 220, a plurality of impellers 230 - 239 (only some of these impellers are labeled), bearings 250 and 255, seals 280 and 285, inlet duct 260 for taking an input process gas at an input pressure (P in ) and outlet duct 270 for expelling the process gas at an output pressure (P out2 ).
- a casing 210 of the compressor 200 covers both the bearings and the seals and prevents the escape of gas from the compressor 200.
- Compressor 200 also includes bearing 290.
- Bearing 290 may be located near the middle between the first and last impellers 230 and 239 in exemplary embodiments.
- the number of impellers 230 - 239 may be increased with the mid-span bearing according to exemplary embodiments than is currently possible for the additional reasons described herein further.
- a limiting factor in the number of stages that can be included in a compressor is the ratio between the length and the diameter of a shaft. This ratio is referred to as the flexibility ratio.
- a compressor may have a maximum flexibility ratio. This ratio can be increased with a longer shaft and a mid-span gas bearing according to exemplary embodiments.
- the gas used in gas bearing 290 may be the gas being processed by compressor 200.
- the placement of gas bearing 290 may be at a location where the rotor displacement for a nearest natural frequency may be most pronounced. This location may be of optimal effectiveness from a rotor dynamic point of view.
- the gas being processed may be "bled" from an output of an impeller that is “downstream” from gas bearing 290 using known elements/components and methods.
- the term downstream is used in this case as it relates to the direction of the gas flow and higher pressure in the case of compressors. That is, pressure is higher downstream and lower upstream relative to a particular location.
- gas bearing 290 is "upstream” relative to impeller 235 but is “downstream” relative to impeller 234.
- the pressure of the working gas coming into bearing 290 has to be at a higher pressure than the pressure of the working gas in "bounding" or "adjacent” stages to the gas bearing so that the gas flow is out of the bearing pad and not into the bearing pads.
- the working gas therefore, has to be bled from a stage that is beyond the location of gas bearing 290. If bearing 290 is placed after five stages (i.e. impeller 234) for example, then the working gas has to be bled from a stage after the sixth stage (i.e. impeller 235). In preferred embodiments, the working gas may be bled from at least two stages downstream from the location of the mid-span gas bearing (i.e. after impeller 236). The high pressure is needed by bearing 290 to work in a stable manner.
- the working gas that is bled from a downstream compression stage may be processed through filter 240 and provided to gas bearing 290 in some embodiments.
- Filter 240 may remove any impurities and particulates in the gas being processed.
- the rotor assembly may be flushed with gas via gas bearing 290 to remove heat from the assembly.
- the percent of working gas mass flow going to the bearing 290 may be less than 0.1 % of the core flow.
- Small bore channels may be provided between bearing 290 and the working flow path.
- the gas from bearing 290 may be lead into the flow path by the bore channel to the proper pressure.
- An increase in the length of the shaft leads to an increase in a ratio of the length to the diameter of the compressor bundle/casing. This facilitates the addition of compression stages within the same casing.
- a method for processing a gas 300 through a multistage compressor having a mid-span gas bearing includes the method steps in the flowchart of FIG. 3 .
- a working gas may be supplied to an inlet duct of a compressor.
- the working gas may be processed by a plurality of compression stages to increase the pressure (and speed) at 320.
- a portion of the working gas may be bled from its flow through the compression stages after it has been processed by a number of compression stages at 330. This number of stages may be greater than one half of the compression stages in the compressor.
- the gas may be supplied to a gas bearing at 340 to flush and remove heat from the rotor assembly, the gas bearing being located upstream of the filter.
- the gas supplied to the gas bearing may be reintroduced into the flow of the working gas at 350.
- Gas from the final stage of compression may be expelled via the outlet duct at 360.
- the gas that has been bled may be processed by a filter to remove any impurities before being provided to the gas bearing.
- the number of mid-span gas bearings may be greater than one. Additional (or, multiple) mid-span gas bearings may be included in some embodiments utilizing the principles described above. Also, a mid-span bearing may not be exactly in the center - it may be offset depending on the particular design and specifications such as having an odd number of stages. Each of the multiple gas bearings may receive working gas from a separate impeller downstream.
- the number of (compression) stages between the input and the first of the gas bearings may be the same as the number stages between the last of the gas bearings and the output.
- the multiple gas bearings may also be spaced apart by the same number of stages. Therefore, the number of stages between the input and the first gas bearing may be the same as the number stages between the first and the second gas bearings (and between each of the subsequent gas bearings) which may also be the same as the number of stages between the last gas bearing and the output, etc.
- the shaft may be a single shaft.
- Exemplary embodiments as described herein provide multiple advantages over compressors that are in use at present. Additional impellers (and longer rotor assembly) may be placed within one casing as opposed to having a series of casings for increasing pressure. Efficiency within each casing (having longer rotor assembly for example) is increased as well. Space requirements for compressors to achieve a particular ratio of output pressure to input pressure are reduced. The flexibility ratio is increased to facilitate additional impellers.
- Length (L2) of shaft 220 in compressor 200 ( FIG. 2 ) is greater than the length (L1) of shaft 120 in compressor 100 ( FIG. 1 )
- gas bearings also obviates the need for elaborate sealing systems within the casing as oil does not enter the casing.
- the cost is also dramatically reduced as a result of the design as described.
Description
- Exemplary embodiments relate generally to compressors and, more specifically, to a mid-span gas bearing in a multistage compressor.
-
JP 2003 293987 A - A compressor is a machine which increases the pressure of a compressible fluid, e.g., a gas, through the use of mechanical energy. Compressors are used in a number of different applications and in a large number of industrial processes, including power generation, natural gas liquification and other processes. Among the various types of compressors used in such processes and process plants are the so-called centrifugal compressors, in which the mechanical energy operates on gas input to the compressor by way of centrifugal acceleration, for example, by rotating a centrifugal impeller.
- Centrifugal compressors can be fitted with a single impeller, i.e., a single stage configuration, or with a plurality of centrifugal stages in series, in which case they are frequently referred to as multistage compressors. Each of the stages of a centrifugal compressor typically includes an inlet volute for gas to be compressed, a rotor which is capable of providing kinetic energy to the input gas and a diffuser which converts the kinetic energy of the gas leaving the impeller into pressure energy.
- A
multistage compressor 100 is illustrated inFIG. 1 .Compressor 100 includes ashaft 120 and a plurality of impellers 130 - 136 (only three of the seven impellers are labeled). Theshaft 120 and impellers 130 - 136 are included in a rotor assembly that is supported throughbearings 150 and 155. - Each of the impellers 130 - 136, which are arranged in sequence, increase the pressure of the process gas. That is,
impeller 130 may increase the pressure from that of gas ininlet duct 160,impeller 131 may increase the pressure of the gas fromimpeller 130,impeller 132 may increase the pressure of the gas fromimpeller 131, etc. Each of these impellers 130 - 136 may be considered to be one stage of themultistage compressor 100. - The multistage
centrifugal compressor 100 operates to take an input process gas frominlet duct 160 at an input pressure (Pin), to increase the process gas pressure through operation of the rotor assembly, and to subsequently expel the process gas throughoutlet duct 170 at an output pressure (Pout1) which is higher than its input pressure. The process gas may, for example, be any one of carbon dioxide, hydrogen sulfide, butane, methane, ethane, propane, liquefied natural gas, or a combination thereof. - The pressurized working fluid within the machine (between
impellers 130 and 136) is sealed from thebearings 150 and 155 usingseals Seals bearings 150 and 155 and leaking out into the atmosphere. Acasing 110 of the compressor is configured so as to cover both the bearings and the seals, and to prevent the escape of gas from thecompressor 100. - While additional stages can provide an increase in the ratio of output pressure to input pressure (i.e. between
inlet 160 and outlet 170), the number of stages cannot simply be increased to obtain a higher ratio. - An increase in the number of stages in a centrifugal compressor leads to multiple problems. The bearings which support the shaft are outside a sealed area that includes the impellers. An increase in the number of stages necessitates a longer shaft. A longer shaft cannot be safely supported by the bearings for the same operating speed, which become further apart as the shaft length increases making the shaft more flexible.
- As the rotor assembly gets longer, the shaft becomes flexible therefore decreasing the rotor natural frequencies. When operating at higher speeds, the decrease in the fundamental natural frequencies of the rotor assembly tends to make the system more susceptible to rotor-dynamic instability, which can limit the operating speed and output of the machine.
- The other issue is the forced response due to synchronous rotor imbalance. When the operating speed coincides with a rotor natural frequency, the machine is defined to be operating at a critical speed, which is a result of rotor imbalance. The compressor must pass through several of these natural frequencies or critical speeds before reaching the design operating speed.
- As the compressor passes through critical speeds, the vibration amplitude of the rotor must be bounded by damping from bearings. However, with a long shaft, the majority of the rotor-dynamic energy is transferred to bend the rotor instead of energy dissipation at the bearings. This results in low damped rotor modes and high amplification factors at rotor resonances that can lead to casing and impeller rubs and even catastrophic failure of the machine.
- At higher speeds past the rotor critical speeds, fluid induced forces are generated between the rotor assembly and the casing (i.e. fluid induced rotor dynamic instability). These pulsations, stemming from fluid forces can excite destructive or even catastrophic vibrations if not adequately dampened. Rotor-dynamic instability is a different mechanism from critical speeds or imbalance response and often time is much more difficult to address.
- It would be desirable to design and provide a multistage centrifugal compressor which includes additional stages without increasing the diameter of the shaft and other design parameters that would drastically change the size and cost of the machine.
- The present invention is defined in the accompanying claims.
- Systems and methods according to these exemplary embodiments provide for an increase in the number of stages in a centrifugal compressor while overcoming problems typically associated with such an increase.
- According to an exemplary embodiment, a centrifugal compressor includes a rotor assembly having a shaft and a plurality of impellers, a pair of bearings located at ends of the shaft and configured to support the rotor assembly, a sealing mechanism disposed between the rotor assembly and the bearings, and a first gas bearing disposed between the plurality of impellers and configured to support the shaft. The first gas bearing receives a working gas from an impeller located downstream from the location of the first gas bearing.
- According to another exemplary embodiment, a method of processing a working gas in a centrifugal compressor includes providing the working gas to an inlet duct of the compressor, processing the gas through a plurality of compression stages with each stage increasing the speed of the gas, bleeding a portion of the accelerated gas after a stage that is downstream from a midway point of the compression stages, providing the bled gas to a bearing, reintroducing the gas from the bearing to the working gas flowing in the compressor, and expelling the working gas from an outlet duct of the compressor.
- According to a further embodiment, a centrifugal compressor includes a rotor assembly having a shaft and a plurality of impellers, a pair of bearings located at ends of the shaft and configured to support the rotor assembly, a sealing mechanism disposed between the rotor assembly and the bearings, and a plurality of gas bearings disposed between the plurality of impellers and configured to support the shaft. The gas bearings receive a working gas from respective impellers located downstream from a location of the gas bearings.
- The accompanying drawings illustrate exemplary embodiments, wherein:
-
FIG. 1 illustrates a multistage centrifugal compressor; -
FIG. 2 illustrates a multistage centrifugal compressor according to exemplary embodiments; and -
FIG. 3 illustrates a method in accordance with exemplary embodiments. - The following detailed description of the exemplary embodiments refers to the accompanying drawings. The same reference numbers in different drawings identify the same or similar elements. Also, the following detailed description does not limit the invention. Instead, the scope of the invention is defined by the appended claims.
- In exemplary embodiments, a mid-span bearing may be utilized to provide additional stiffness to the rotor assembly with a longer shaft to overcome the critical speed issue highlighted above. Such a bearing makes the rotor assembly less flexible and therefore allows the rotor-dynamic energy (due to synchronous rotor imbalance forces) to be transmitted to the bearings.
- This "three-bearing" configuration increases the damping in the rotor modes and lowers amplification factors as the rotor traverses through the critical speed allowing for safe operation of the rotor assembly. A mid-span bearing may, therefore, be provided within the casing for facilitating an increased number of stages (i.e. longer shaft) and overcoming the rotor dynamic instability.
- Surface speed of a shaft (such as shaft 120) is a function of its diameter. The diameter in the middle portion of the shaft is greater than the diameter at the end portions. The difference in speeds between these portions (i.e. between middle and end) may be in the order of 2 to 3 times. Therefore, the surface speed of a shaft is greater (by a factor of 2 to 3) at the center portion of the shaft than it is at the end portions.
- Bearings, such as
bearing 150 and 155 ofFIG. 1 may typically be oil bearings. Oil bearings, however, are limited to usage where surface speed is typically closer to the surface speed at end portions of the shaft. - A mid-span bearing according to exemplary embodiments may be a gas bearing. Gas bearings can be used where surface speed is closer to the surface speeds at middle portions of a shaft.
- In existing systems, highly corrosive working fluids such as hydrogen disulfide can damage conventional oil lubricated journal bearings. Such damage, greatly limits the life of the machine as oil lubricated bearings are not resistant to corrosive gases. A process gas lubricated bearing, however, does not require such sealing and can operate even in this corrosive environment while maintaining the life of the machine.
- In addition to having ultra high surface speed viscous fluid capability, there is negligible power loss with gas bearings relative to oil bearings. Oil bearings also require sealing systems for preventing leakage of oil into the gas being processed by the compressor. Gas bearings obviate this need for sealing systems.
-
FIG. 2 illustrates a compressor according to exemplary embodiments.Compressor 200 includes ashaft 220, a plurality of impellers 230 - 239 (only some of these impellers are labeled),bearings seals inlet duct 260 for taking an input process gas at an input pressure (Pin) andoutlet duct 270 for expelling the process gas at an output pressure (Pout2). Acasing 210 of thecompressor 200 covers both the bearings and the seals and prevents the escape of gas from thecompressor 200. -
Compressor 200 also includesbearing 290. Bearing 290 may be located near the middle between the first andlast impellers - Currently, a limiting factor in the number of stages that can be included in a compressor is the ratio between the length and the diameter of a shaft. This ratio is referred to as the flexibility ratio. In order to operate effectively, a compressor may have a maximum flexibility ratio. This ratio can be increased with a longer shaft and a mid-span gas bearing according to exemplary embodiments.
- The gas used in
gas bearing 290 may be the gas being processed bycompressor 200. The placement ofgas bearing 290 may be at a location where the rotor displacement for a nearest natural frequency may be most pronounced. This location may be of optimal effectiveness from a rotor dynamic point of view. - The gas being processed may be "bled" from an output of an impeller that is "downstream" from gas bearing 290 using known elements/components and methods. The term downstream is used in this case as it relates to the direction of the gas flow and higher pressure in the case of compressors. That is, pressure is higher downstream and lower upstream relative to a particular location. For example, as illustrated in
FIG. 2 , gas bearing 290 is "upstream" relative toimpeller 235 but is "downstream" relative toimpeller 234. - The pressure of the working gas coming into
bearing 290 has to be at a higher pressure than the pressure of the working gas in "bounding" or "adjacent" stages to the gas bearing so that the gas flow is out of the bearing pad and not into the bearing pads. - The working gas, therefore, has to be bled from a stage that is beyond the location of
gas bearing 290. If bearing 290 is placed after five stages (i.e. impeller 234) for example, then the working gas has to be bled from a stage after the sixth stage (i.e. impeller 235). In preferred embodiments, the working gas may be bled from at least two stages downstream from the location of the mid-span gas bearing (i.e. after impeller 236). The high pressure is needed by bearing 290 to work in a stable manner. - The working gas that is bled from a downstream compression stage may be processed through
filter 240 and provided togas bearing 290 in some embodiments.Filter 240 may remove any impurities and particulates in the gas being processed. The rotor assembly may be flushed with gas viagas bearing 290 to remove heat from the assembly. The percent of working gas mass flow going to thebearing 290 may be less than 0.1 % of the core flow. - Small bore channels may be provided between
bearing 290 and the working flow path. The gas from bearing 290 may be lead into the flow path by the bore channel to the proper pressure. - An increase in the length of the shaft leads to an increase in a ratio of the length to the diameter of the compressor bundle/casing. This facilitates the addition of compression stages within the same casing.
- Thus, according to an exemplary embodiment, a method for processing a
gas 300 through a multistage compressor having a mid-span gas bearing includes the method steps in the flowchart ofFIG. 3 . At 310, a working gas may be supplied to an inlet duct of a compressor. The working gas may be processed by a plurality of compression stages to increase the pressure (and speed) at 320. A portion of the working gas may be bled from its flow through the compression stages after it has been processed by a number of compression stages at 330. This number of stages may be greater than one half of the compression stages in the compressor. - The gas may be supplied to a gas bearing at 340 to flush and remove heat from the rotor assembly, the gas bearing being located upstream of the filter. The gas supplied to the gas bearing may be reintroduced into the flow of the working gas at 350. Gas from the final stage of compression may be expelled via the outlet duct at 360. In some embodiments, the gas that has been bled may be processed by a filter to remove any impurities before being provided to the gas bearing.
- The number of mid-span gas bearings may be greater than one. Additional (or, multiple) mid-span gas bearings may be included in some embodiments utilizing the principles described above. Also, a mid-span bearing may not be exactly in the center - it may be offset depending on the particular design and specifications such as having an odd number of stages. Each of the multiple gas bearings may receive working gas from a separate impeller downstream.
- If multiple gas bearings are implemented within a compressor, the number of (compression) stages between the input and the first of the gas bearings may be the same as the number stages between the last of the gas bearings and the output. The multiple gas bearings may also be spaced apart by the same number of stages. Therefore, the number of stages between the input and the first gas bearing may be the same as the number stages between the first and the second gas bearings (and between each of the subsequent gas bearings) which may also be the same as the number of stages between the last gas bearing and the output, etc.
- A first of the gas bearings may receive compressed gas from a stage that is both downstream from the first gas bearing and upstream from a second of the gas bearings. That is, the first gas bearing may receive compressed gas from a stage that is between the first and the second gas bearings.
- Those skilled in the art will appreciate that the specific number of impellers described above and illustrated in
FIG. 2 are purely exemplary and that other number of impellers may be used. There may be a greater or a lesser number impellers depending on the application. The shaft may be a single shaft. - Exemplary embodiments as described herein provide multiple advantages over compressors that are in use at present. Additional impellers (and longer rotor assembly) may be placed within one casing as opposed to having a series of casings for increasing pressure. Efficiency within each casing (having longer rotor assembly for example) is increased as well. Space requirements for compressors to achieve a particular ratio of output pressure to input pressure are reduced. The flexibility ratio is increased to facilitate additional impellers.
- Length (L2) of
shaft 220 in compressor 200 (FIG. 2 ) according to exemplary embodiments is greater than the length (L1) ofshaft 120 in compressor 100 (FIG. 1 ) - In addition, the use of gas bearings also obviates the need for elaborate sealing systems within the casing as oil does not enter the casing. The cost is also dramatically reduced as a result of the design as described.
- The above-described exemplary embodiments are intended to be illustrative in all respects, rather than restrictive, of the present invention. Thus the present invention is capable of many variations in detailed implementation that can be derived from the description contained herein by a person skilled in the art. All such variations and modifications are considered to be within the scope of the present invention as defined by the following claims. No element, act, or instruction used in the description of the present application should be construed as critical or essential to the invention unless explicitly described as such. Also, as used herein, the article "a" is intended to include one or more items.
Claims (14)
- A centrifugal compressor (200) comprising:a rotor assembly including a shaft (220) and a plurality of impellers (230-239);a pair of bearings (250,255) located at ends of the shaft (220) and configured to support the rotor assembly;a sealing mechanism (280,285) disposed between the rotor assembly and the bearings;a first gas bearing (290) disposed between the plurality of impellers (230-239) and configured to support the shaft (220), the gas bearing receiving a working gas from an impeller located downstream from a location of the first gas bearing; characterised bya filter (240) for purifying the working gas before the working gas is received by the gas bearing (290).
- The centrifugal compressor of claim 1, wherein the first gas bearing (290) is located at a point that is half way between the plurality of impellers in the compressor.
- The centrifugal compressor of claim 1 or claim 2, wherein the first gas bearing (290) is located at a point that is beyond a half way between the plurality of impellers in the compressor.
- The centrifugal compressor of any preceding claim, wherein the working gas is one of carbon dioxide, hydrogen sulfide, butane, methane, ethane, propane, liquefied natural gas, or a combination thereof.
- The centrifugal compressor of any preceding claim, wherein the pair of bearings (250,255) are oil bearings.
- The centrifugal compressor of claim 5, wherein an operating surface speed of the gas bearings (290) is higher than an operating surface speed of the oil bearings (250,255).
- The centrifugal compressor of claim 6, wherein the operating surface speed of the gas bearing (290) is at least twice the operating surface speed of the oil bearing (250,255).
- The centrifugal compressor of any preceding claim, further comprising:a second gas bearing (290) disposed between the plurality of impellers, the second bearing being located downstream from the first gas bearing.
- The centrifugal compressor of any preceding claim, wherein the working gas is received by the first gas bearing (290) from an impeller that is one compression stage beyond the first gas bearing.
- The centrifugal compressor of any preceding claim, wherein the working gas is received by the first gas bearing (290) from an impeller that is at least two compression stages beyond the first gas bearing.
- The centrifugal compressor of any preceding claim, wherein the working gas received by the first gas bearing is less than 0.1 % of working gas flowing through the compressor.
- The centrifugal compressor of any preceding claim, wherein the shaft (220) is a single shaft.
- A method of processing a working gas in a centrifugal compressor, the method comprising the steps of:providing the working gas to an inlet duct of the compressor;processing the gas through a plurality of compression stages, each stage increasing the speed of the gas;bleeding a portion of the accelerated gas after a stage that is downstream from a midway point of the compression stages;providing the bled gas to a gas bearing (290) located between the plurality of compression stages;reintroducing the gas from the gas bearing to the working gas flowing in the compressor; andexpelling the working gas from an outlet duct of the compressor, characterised by filtering the gas that has been bled to remove impurities before providing it to the gas bearing.
- The centrifugal compressor (200) of claim 1, wherein
a plurality of further gas bearings (290) are disposed between the plurality of impellers and configured to support the shaft (220), each of the gas bearings receiving a working gas from a respective impeller located downstream from a location of the gas bearing; and
a filter (240) for purifying the working gas before the working gas is received by the gas bearing (290).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITCO2009A000067A IT1396885B1 (en) | 2009-12-17 | 2009-12-17 | INTERMEDIATE GAS BEARING |
PCT/EP2010/069347 WO2011080047A2 (en) | 2009-12-17 | 2010-12-10 | Mid-span gas bearing |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2513489A2 EP2513489A2 (en) | 2012-10-24 |
EP2513489B1 true EP2513489B1 (en) | 2016-12-07 |
Family
ID=42556516
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10787786.2A Active EP2513489B1 (en) | 2009-12-17 | 2010-12-10 | Mid-span gas bearing |
Country Status (12)
Country | Link |
---|---|
US (1) | US9169846B2 (en) |
EP (1) | EP2513489B1 (en) |
JP (1) | JP5802216B2 (en) |
KR (1) | KR20120115324A (en) |
CN (1) | CN102753834B (en) |
AU (1) | AU2010338504B2 (en) |
BR (1) | BR112012015041A2 (en) |
CA (1) | CA2784521A1 (en) |
IT (1) | IT1396885B1 (en) |
MX (1) | MX2012007101A (en) |
RU (1) | RU2552880C2 (en) |
WO (1) | WO2011080047A2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017211033A1 (en) * | 2017-06-29 | 2019-01-03 | Robert Bosch Gmbh | Compressor device and electric machine |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9429191B2 (en) | 2013-10-11 | 2016-08-30 | General Electric Company | Journal bearing assemblies and methods of assembling same |
US9121448B2 (en) | 2013-10-11 | 2015-09-01 | General Electric Company | Hermetically sealed damper assembly and methods of assembling same |
US9856886B2 (en) * | 2015-01-08 | 2018-01-02 | Honeywell International Inc. | Multistage radial compressor baffle |
FR3038665B1 (en) * | 2015-07-07 | 2017-07-21 | Danfoss Commercial Compressors | CENTRIFUGAL COMPRESSOR HAVING INTER-STAGE SEALING ARRANGEMENT |
US10718346B2 (en) * | 2015-12-21 | 2020-07-21 | General Electric Company | Apparatus for pressurizing a fluid within a turbomachine and method of operating the same |
US10036279B2 (en) * | 2016-04-18 | 2018-07-31 | General Electric Company | Thrust bearing |
US10001166B2 (en) | 2016-04-18 | 2018-06-19 | General Electric Company | Gas distribution labyrinth for bearing pad |
US9951811B2 (en) | 2016-04-18 | 2018-04-24 | General Electric Company | Bearing |
US10914195B2 (en) | 2016-04-18 | 2021-02-09 | General Electric Company | Rotary machine with gas bearings |
US10577975B2 (en) | 2016-04-18 | 2020-03-03 | General Electric Company | Bearing having integrally formed components |
US9746029B1 (en) | 2016-04-18 | 2017-08-29 | General Electric Company | Bearing |
US10066505B2 (en) | 2016-04-18 | 2018-09-04 | General Electric Company | Fluid-filled damper for gas bearing assembly |
US11193385B2 (en) | 2016-04-18 | 2021-12-07 | General Electric Company | Gas bearing seal |
NO342066B1 (en) * | 2016-06-03 | 2018-03-19 | Vetco Gray Scandinavia As | Modular stackable compressor with gas bearings and system for raising the pressure in production gas |
JP6908472B2 (en) * | 2017-08-31 | 2021-07-28 | 三菱重工コンプレッサ株式会社 | Centrifugal compressor |
JP6963471B2 (en) * | 2017-11-09 | 2021-11-10 | 三菱重工コンプレッサ株式会社 | Rotating machine |
US11692479B2 (en) | 2019-10-03 | 2023-07-04 | General Electric Company | Heat exchanger with active buffer layer |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0302317A1 (en) | 1987-08-03 | 1989-02-08 | INTERATOM Gesellschaft mit beschränkter Haftung | Static and dynamic gas bearing |
DE4327506A1 (en) | 1992-08-19 | 1994-02-24 | Hitachi Ltd | Turbo vacuum pump assembly - has housing with suction and delivery apertures and contg. evacuating pump which compresses gas sucked in through suction aperture |
JPH07208456A (en) | 1994-01-20 | 1995-08-11 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor |
JPH1061592A (en) | 1996-08-15 | 1998-03-03 | Mitsubishi Heavy Ind Ltd | Seal device for fluid machinery |
JPH1113687A (en) | 1997-06-20 | 1999-01-19 | Daikin Ind Ltd | Turbo machinery |
WO1999031390A1 (en) | 1997-12-03 | 1999-06-24 | Sundyne Corporation | Method for generating over-pressure gas |
JP2003293987A (en) | 2002-04-01 | 2003-10-15 | Mitsubishi Heavy Ind Ltd | Fluid machinery and rotor installed therein |
EP1559915A1 (en) | 2004-01-29 | 2005-08-03 | Pfeiffer Vacuum GmbH | Gas friction pump |
WO2007110281A1 (en) | 2006-03-24 | 2007-10-04 | Siemens Aktiengesellschaft | Compressor unit |
WO2008018800A1 (en) | 2006-08-08 | 2008-02-14 | Statoil Asa | Bearing system for rotor in rotating machines |
DE102006037821A1 (en) | 2006-08-12 | 2008-02-14 | Atlas Copco Energas Gmbh | turbomachinery |
US20090246048A1 (en) | 2008-03-26 | 2009-10-01 | Ebara Corporation | Turbo vacuum pump |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5102237A (en) | 1976-05-29 | 1992-04-07 | Ide Russell D | Self positioning beam mounted bearing and bearing and shaft assembly including the same |
SU1173072A1 (en) * | 1984-02-17 | 1985-08-15 | Производственное Объединение "Калужский Турбинный Завод" | Shaft bearing |
US5066144A (en) | 1989-02-08 | 1991-11-19 | Ide Russell D | Hydrodynamic bearings having a continuous beam mounted support surface |
SU1590677A1 (en) * | 1988-11-24 | 1990-09-07 | Уральский филиал Всесоюзного теплотехнического научно-исследовательского института им.Ф.Э.Дзержинского | Centrifugal pump |
GB0117941D0 (en) * | 2001-07-24 | 2001-09-19 | Weir Pumps Ltd | Pump assembly |
DE502007004562D1 (en) * | 2007-06-28 | 2010-09-09 | Siemens Ag | Shaft seal for a turbomachine |
-
2009
- 2009-12-17 IT ITCO2009A000067A patent/IT1396885B1/en active
-
2010
- 2010-12-10 CN CN201080064076.0A patent/CN102753834B/en active Active
- 2010-12-10 CA CA2784521A patent/CA2784521A1/en not_active Abandoned
- 2010-12-10 WO PCT/EP2010/069347 patent/WO2011080047A2/en active Application Filing
- 2010-12-10 BR BR112012015041A patent/BR112012015041A2/en not_active IP Right Cessation
- 2010-12-10 AU AU2010338504A patent/AU2010338504B2/en not_active Ceased
- 2010-12-10 EP EP10787786.2A patent/EP2513489B1/en active Active
- 2010-12-10 MX MX2012007101A patent/MX2012007101A/en not_active Application Discontinuation
- 2010-12-10 KR KR1020127018710A patent/KR20120115324A/en not_active Application Discontinuation
- 2010-12-10 RU RU2012124833/06A patent/RU2552880C2/en active
- 2010-12-10 JP JP2012543624A patent/JP5802216B2/en active Active
- 2010-12-10 US US13/516,393 patent/US9169846B2/en active Active
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0302317A1 (en) | 1987-08-03 | 1989-02-08 | INTERATOM Gesellschaft mit beschränkter Haftung | Static and dynamic gas bearing |
DE4327506A1 (en) | 1992-08-19 | 1994-02-24 | Hitachi Ltd | Turbo vacuum pump assembly - has housing with suction and delivery apertures and contg. evacuating pump which compresses gas sucked in through suction aperture |
JPH07208456A (en) | 1994-01-20 | 1995-08-11 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor |
JPH1061592A (en) | 1996-08-15 | 1998-03-03 | Mitsubishi Heavy Ind Ltd | Seal device for fluid machinery |
JPH1113687A (en) | 1997-06-20 | 1999-01-19 | Daikin Ind Ltd | Turbo machinery |
WO1999031390A1 (en) | 1997-12-03 | 1999-06-24 | Sundyne Corporation | Method for generating over-pressure gas |
JP2003293987A (en) | 2002-04-01 | 2003-10-15 | Mitsubishi Heavy Ind Ltd | Fluid machinery and rotor installed therein |
EP1559915A1 (en) | 2004-01-29 | 2005-08-03 | Pfeiffer Vacuum GmbH | Gas friction pump |
WO2007110281A1 (en) | 2006-03-24 | 2007-10-04 | Siemens Aktiengesellschaft | Compressor unit |
WO2008018800A1 (en) | 2006-08-08 | 2008-02-14 | Statoil Asa | Bearing system for rotor in rotating machines |
DE102006037821A1 (en) | 2006-08-12 | 2008-02-14 | Atlas Copco Energas Gmbh | turbomachinery |
US20090246048A1 (en) | 2008-03-26 | 2009-10-01 | Ebara Corporation | Turbo vacuum pump |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017211033A1 (en) * | 2017-06-29 | 2019-01-03 | Robert Bosch Gmbh | Compressor device and electric machine |
Also Published As
Publication number | Publication date |
---|---|
BR112012015041A2 (en) | 2017-03-01 |
ITCO20090067A1 (en) | 2011-06-18 |
EP2513489A2 (en) | 2012-10-24 |
JP2013514484A (en) | 2013-04-25 |
JP5802216B2 (en) | 2015-10-28 |
WO2011080047A2 (en) | 2011-07-07 |
KR20120115324A (en) | 2012-10-17 |
RU2012124833A (en) | 2014-01-27 |
US20130195609A1 (en) | 2013-08-01 |
CA2784521A1 (en) | 2011-07-07 |
WO2011080047A3 (en) | 2011-09-09 |
AU2010338504A1 (en) | 2012-07-12 |
AU2010338504B2 (en) | 2016-03-10 |
RU2552880C2 (en) | 2015-06-10 |
US9169846B2 (en) | 2015-10-27 |
MX2012007101A (en) | 2012-09-07 |
IT1396885B1 (en) | 2012-12-20 |
CN102753834A (en) | 2012-10-24 |
CN102753834B (en) | 2016-04-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2513489B1 (en) | Mid-span gas bearing | |
US9347459B2 (en) | Abradable seal with axial offset | |
EP2737179B1 (en) | Centrifugal impeller and turbomachine | |
EP2472123A1 (en) | Systems and methods for swirl brake tapering | |
EP2734735B1 (en) | Multistage centrifugal turbomachine | |
EP2386763A2 (en) | Balancing piston | |
US20170130737A1 (en) | Rotary machine | |
US20180223869A1 (en) | Turbomachine and method of operating a turbomachine | |
CN209838754U (en) | Compressor with gas bearing | |
JP2021089072A (en) | Journal and thrust gas bearing |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20120717 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAX | Request for extension of the european patent (deleted) | ||
17Q | First examination report despatched |
Effective date: 20140813 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R079 Ref document number: 602010038665 Country of ref document: DE Free format text: PREVIOUS MAIN CLASS: F04D0029100000 Ipc: F04D0017120000 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04D 17/12 20060101AFI20160622BHEP |
|
INTG | Intention to grant announced |
Effective date: 20160720 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: AT Ref legal event code: REF Ref document number: 852002 Country of ref document: AT Kind code of ref document: T Effective date: 20161215 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 7 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602010038665 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NO Ref legal event code: T2 Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170308 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20161231 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170407 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170407 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170307 Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R026 Ref document number: 602010038665 Country of ref document: DE |
|
PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PLAX | Notice of opposition and request to file observation + time limit sent |
Free format text: ORIGINAL CODE: EPIDOSNOBS2 |
|
26 | Opposition filed |
Opponent name: SIEMENS AKTIENGESELLSCHAFT Effective date: 20170907 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20161210 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20161210 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
PLBB | Reply of patent proprietor to notice(s) of opposition received |
Free format text: ORIGINAL CODE: EPIDOSNOBS3 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20101210 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20161210 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R100 Ref document number: 602010038665 Country of ref document: DE |
|
PLCK | Communication despatched that opposition was rejected |
Free format text: ORIGINAL CODE: EPIDOSNREJ1 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: UEP Ref document number: 852002 Country of ref document: AT Kind code of ref document: T Effective date: 20161207 |
|
PLBN | Opposition rejected |
Free format text: ORIGINAL CODE: 0009273 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: OPPOSITION REJECTED |
|
27O | Opposition rejected |
Effective date: 20190212 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161207 |
|
REG | Reference to a national code |
Ref country code: NO Ref legal event code: CHAD Owner name: NUOVO PIGNONE INTERNATIONAL S.R.L., IT |
|
REG | Reference to a national code |
Ref country code: NO Ref legal event code: CHAD Owner name: NUOVO PIGNONE TECNOLOGIE - S.R.L., IT |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PK Free format text: BERICHTIGUNGEN |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20220728 AND 20220803 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20221122 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CH Payment date: 20230101 Year of fee payment: 13 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: PC Ref document number: 852002 Country of ref document: AT Kind code of ref document: T Owner name: NUOVO PIGNONE TECNOLOGIE - S.R.L., IT Effective date: 20230601 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20231121 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NO Payment date: 20231123 Year of fee payment: 14 Ref country code: FR Payment date: 20231122 Year of fee payment: 14 Ref country code: DE Payment date: 20231121 Year of fee payment: 14 Ref country code: AT Payment date: 20231123 Year of fee payment: 14 |